JPS60263731A - Controlling device for working oil pressure for frictional engaging device - Google Patents

Abstract

PURPOSE:To enable the common use of parts with which a feed oil passage and a communicating passage are formed, by a method wherein plugs, with which a passage with a pore serving as an orifice is formed, are additionally provided, and the plugs are attached to a feed oil passage and a communicating passage. CONSTITUTION:By replacing plugs 60 and 70 attached to a feed oil passage 44 and a communicating passage 20, control properties of a frictional engaging device 32 can be varied. Thus, the plugs 60 and 70 are selectively attached so that a working timing is adjusted to an optimum valve depending on combination of the device and an engine and a device-mounted vehicle, and this enables the working timing of the frictional engaging device 32 to be always held at an optimum value. Orifices, set in various sizes in order to set an optimum working timing, are formed in the plugs 60 and 70, and the plugs 60 and 70 are attached to the feed oil passage 44 and the communication passage 20. Thus, the use of the same part will suffice for constitution of a rotary shaft 40, and this enables the common use of part.

Description

[Detailed description of the invention] The present invention relates to a hydraulic pressure control device for a frictional engagement device.

More specifically, the present invention relates to a hydraulic pressure control device for a friction engagement device of a brake device or a clutch/nochi device used in a transmission such as an automatic transmission.

[Prior art]

Automatic transmissions installed in vehicles such as automobiles generally use a brake device or a flanch device formed of a frictional engagement device (Japanese Patent Publication No. 1.0315/1982).

The piston is slidably fitted into the cylinder. A chamber is formed between the cylinder and the piston, and when hydraulic pressure is supplied to this chamber, the piston is actuated and the frictional engagement device is brought into engagement.

The piston is in a frictional engagement state, and the actuation of the piston to the frictional engagement state quickly closes the clearance, thereby bringing the frictional engagement device into the engagement state and completing the gear shifting operation, and then, It is generally considered preferable to maintain this state of frictional engagement with a strong pressing force.

A possible way to achieve this preferable operation is to divide the chamber in which the piston is operated into a first chamber and a second chamber, and supply hydraulic pressure from the first chamber to the second chamber. (unknown before this application).

In this case, the first chamber is formed as a small-volume annular chamber at a radially inner position, and the second chamber is formed as a large-volume annular chamber at a radially outer position. A supply oil passage through which hydraulic pressure is supplied is connected to the first chamber, and a communication passage is formed between the first chamber and the second chamber. Therefore, the hydraulic pressure is first supplied to the first chamber through the supply oil passage, and the hydraulic pressure supplied to the first chamber is supplied to the second chamber via the communication passage. Therefore, the piston first quickly closes the clearance of the frictional engagement device by the hydraulic pressure supplied to the small-capacity first chamber, brings the frictional engagement device into the engaged state, and then the large-capacity first chamber. The hydraulic pressure supplied to the second chamber is also added to maintain the engaged state with a strong pressing force.

Incidentally, the operating timing and operating oil pressure of the friction engagement device are adjusted by the size of the orifice diameter formed in the supply oil passage and the communication passage that supply the operating oil pressure to the first chamber and the second chamber, and are adjusted to the optimum value. The size of the orifice diameter is set to match the operating timing and operating oil pressure.

However, this operating timing is different even for the same transmission.
The size of the orifice formed in the supply oil passage and the communication passage generally varies depending on the combination with the engine or the vehicle in which it is installed.

Therefore, it is necessary to set many types of parts for forming supply oil passages and communication only due to the difference in orifice diameter, and there is a problem that it is impossible to standardize the parts.

The reason why it is difficult to standardize parts is that the orifice is integrally formed with the supply oil passage and the communication passage.

[Problem that the invention seeks to solve]

Therefore, the problem to be solved by the present invention is that only the passage for the small hole serving as the orifice is formed as a separate part and installed, so that the parts forming the supply oil passage and the communication passage are common to each other. The aim is to achieve this goal.

[Means for solving problems]

In order to solve the above-mentioned problems, the hydraulic pressure control device for a frictional engagement device according to the present invention is such that, in the hydraulic pressure control device for a frictional engagement device of this kind described above, the supply oil path and the communication path are equipped with plugs. Provision is then made for a plug to be selected and installed which is shaped so that it is possible to do so and has a small hole passage serving as an orifice.

[Effect]

Depending on the engine to which the transmission is combined or the vehicle in which it is mounted, various types of small hole passages serving as orifices are preset in the supply oil passages and communication passages to the first chamber and the second chamber. A desired plug is selected from among the selected plugs and installed, and the frictional engagement device is operated at an optimal timing.

〔Effect of the invention〕

As described above, the present invention separately provides a plug that forms the passage of the small hole that becomes the orifice, and this plug is attached to the supply oil passage and the communication passage, so that the supply oil passage and the communication passage are formed. Only one type of parts is required, and parts can be standardized.

,〔Example〕 Embodiments of the present invention will be described below based on the drawings.

1 to 3 show an embodiment of a hydraulic pressure control device for a frictional engagement device according to the present invention. This embodiment shows a case where the frictional engagement device is a clutch device.

A piston 12 is slidably fitted into the cylinder 10. The cylinder 10 is formed by coupling a clutch drum 11 and a shaft end portion 41 of a rotating shaft 40. cylinder 1
0 is equipped with a partition part 14, and cylinder IO and piston 1
2 is partitioned by this partition part 14 and the first
A chamber 16 and a second chamber 18 are formed. The first chamber 16 is located radially inward and is formed into a small volume annular chamber. The second chamber 18 is located at a radially outer location and is formed into a large volume annular chamber.

The rotating shaft 40 is provided with a main oil passage 42 for hydraulic pressure and a supply oil passage 44 to the first chamber 16.
4 is coupled to the first chamber 16. Further, a communication passage 20 is provided in the partition portion 14 of the cylinder 10, and communicates the first chamber 16 and the second chamber 18. As a result, the hydraulic pressure is first supplied from the main oil passage 42 to the first chamber 16 through the supply oil passage 44, and then from the first chamber 16 to the second chamber 18.
is supplied through the communication path 20.

A plug 6° is attached to the supply oil passage 44 and the communication passage 20. The plugs 60, 70 each have a small hole passageway 62, 72 that serves as an orifice. As a result, the hydraulic pressure is transferred from the supply oil path 44 and the communication path 70 to the first chamber 16 and the second chamber 18.
When supplied to the piston 12, it is controlled by the passage 62.72 of the plug 60.70 which serves as an orifice.
operation is controlled.

FIG. 3 shows various shapes of plugs 60, 70.

In FIG. 181, the entire passage 62, 72 is formed as a small orifice. (Figure b1 and (Figure C1) show an example in which a part of the passage 62.72 is formed into a small hole that becomes an orifice, and figure !b1 is an example in which a small hole is provided at the end.
Figure C1 is an example in which a small hole is provided in the center. In addition, lb1
When installed as shown in the figure and tc1 figure, the viscosity coefficient is not affected by the oil temperature, and the seal El'7 at low temperature and high temperature is
This has the advantage that there is little variation in level. There are many types of plugs 60, 70 with different sizes of small holes serving as orifices, and the plugs 60, 70 are appropriately selected and installed depending on the engine to which the transmission is combined or the vehicle in which the transmission is mounted.

Returning to FIG. 1, a spring seat 46 is fixedly attached to the tip portion 40a of the rotating shaft 40. A return spring 48 formed of a coil spring is interposed and attached between this spring seat 46 and a spring seat 56 seated on the piston 12.

This return spring 48 always biases the piston 12 in the left direction as viewed in FIG. Therefore, when no hydraulic pressure is supplied to the r-th chamber 16 and the second chamber 18, the piston 12 is brought into contact with the side wall 10a of the cylinder 10 as shown in FIG.

In addition, in FIG. 1, the seal rings 26 and 28 attached to the piston 12 and the seal ring 30 attached to the partition portion 14 ensure an oil-tight state of the first chamber 16 and the second chamber 18. , prevents hydraulic pressure from leaking to other areas.

The friction engagement device 32 is formed by a large number of friction materials 34 and disk plates 36 arranged alternately. That is, it is formed in a multi-plate format. As is well known, each friction material 34 has an inner peripheral portion connected to the hub 5 of another rotation transmission member 50.
2 is attached by a claw connection so that it is integral in the rotational direction but movable in the axial direction. Similarly, each disk plate 36 is attached at its outer circumferential portion to the outer circumferential wall portion 10b of the cylinder 10 by claw coupling so as to be integral in the rotational direction but movable in the axial direction.

The frictional engagement device 32 is stopped by a snap ring 54 attached to the outer peripheral wall portion 10b4 of the cylinder IOQ, and is prevented from being pulled out. Further, a disk spring 38 is provided on the side of the friction engagement device 32 that comes into contact with the piston 12.
is installed.

The frictional engagement device 32 is pressed by the piston 12,
When a frictional force is generated between the disk plate 36 and the friction material 34, a frictional engagement state is created, and the rotation shaft 42 and the rotation transmission member 50 are brought into a rotation transmission state. And piston 12
As a result, the frictional engagement device 32 is released from the frictional engagement state, and the rotating shaft 40 and the rotation transmission member 50 are disconnected from each other.

Next, the effect will be explained.

When the frictional engagement device 32 is brought into the frictional engagement state,
The hydraulic pressure is supplied from the main oil passage 42 to the first chamber 16 through the supply oil passage 44, and is further supplied from the first chamber 16 to the second chamber 18 via the communication passage 20. As a result, the piston 12 is actuated, and the friction engagement device 32 is brought into a friction engagement state.

In detail, the operation of the piston 12 is performed when the hydraulic pressure is first
Since the hydraulic pressure is supplied to the first chamber 16, the hydraulic pressure is supplied to the first chamber 16. 1st
Since the chamber 16 has a small capacity, a large stroke operation is quickly performed with a small amount of hydraulic pressure, and this operation closes the clearance of the frictional engagement device 32 to bring it into a frictional engagement state that achieves a speed change state.

Next, when the second chamber 18 is filled with the hydraulic pressure supplied through the communication passage 20, the piston 12 is also pressurized with the hydraulic pressure from the second chamber 18, and the friction engagement device 32 is maintained in a frictionally engaged state with a strong pressing force, and the frictionally engaged device 32 is brought into a complete frictionally engaged state without slipping.

The friction engagement device 32, such as the increase in the hydraulic pressure supplied to the first chamber 16 and the second chamber I8 described above, and the timing of transition from the friction engagement state to the complete friction engagement state for achieving the gear shift state. The operation timing is based on supply oil path 4.
4 and the orifice of a plug 60, 70 mounted in the communication passage 20. FIG. 4 shows its control characteristic diagram, where diagram A shows the hydraulic characteristic of the first chamber 16 and diagram B shows the hydraulic characteristic of the second chamber 18. FIG. 4 shows changes in hydraulic characteristics due to differences in the plugs 60 installed in the supply oil path 44.

The solid line indicates the case where the orifice diameter provided in the plug 60 is large, and the broken line indicates the case where the orifice diameter is small. Furthermore, FIG. 5 shows changes in hydraulic characteristics due to differences in the plugs 70 installed in the communication passage 20. In the case of this Fig. 5 as well, the solid line is the plug 70.
This is the case where the diameter of the orifice provided is large, and the broken line is small.

FIG. 6 shows a change diagram of the frictional engagement device 32 based on this control.

In this way, by changing the plugs 60 and 70 attached to the supply oil path 44 and the communication path 20, the friction engagement device 32
Since the control characteristics of the friction engagement device 32 can be changed, if the plugs 60 and 70 are selected and installed to achieve the optimal activation timing depending on the combination with the engine or the vehicle in which it is installed, the control characteristics of the friction engagement device 32 can be changed. The actuation timing can always be set to the optimum actuation timing.

In this way, the plug 60.7 has orifices of various sizes set in order to set the optimal operation timing.
0, and this plug 60.70 is connected to the supply oil passage 44,
and the communication passage 20, so the communication
The member in which the passage 20 and the supply oil passage 44 are formed, the rotary shaft 40 in this embodiment, can be the same part, and the parts can be made common.

Note that the above-described operation of the frictional engagement device 32 is released by first discharging the hydraulic pressure of the first chamber 16 to the main oil passage 42 through the supply oil passage 44, and then discharging the hydraulic pressure of the second chamber 18. is returned to the first chamber]6 via the passage 20,
By exhausting the pressure from the first chamber 16, the piston 12 is moved back and deactivated.

FIG. 7 shows a modification of the embodiment described above.

The plug 70 attached to the communication path 204 is arranged in the axial direction. In the embodiment described above, since the plugs 70 are disposed in the radial direction, the hydraulic pressure is applied to the plugs 70.
When flowing through the passage 72, it is affected by centrifugal force, which may cause problems such as the control state changing depending on the rotation state. However, by arranging it in the axial direction,
It is not affected by centrifugal force and can be controlled accurately.

[Brief explanation of the drawing]

1 to 3 show an embodiment of the hydraulic pressure control device for a frictional engagement device according to the present invention, in which FIG. 1 is a cross-sectional view, and FIG. 2 is a side view of the cylinder portion. Figure 7

Claims (1)

[Claims] 1. A piston that operates the frictional engagement device is slidably fitted into a cylinder, and a working hydraulic pressure is supplied between the piston and the cylinder, and a first chamber and a second chamber are configured to actuate the piston. A supply oil passage through which hydraulic pressure is supplied is connected to the first chamber, and a communication passage is provided between the first chamber and the second chamber. , a hydraulic pressure control device for a frictional engagement device in which hydraulic pressure supplied to the first chamber through the supply oil passage is supplied to the second chamber via the communication passage; a plug can be attached to the supply oil passage and the communication passage; 1. A hydraulic pressure control device for a frictional engagement device, characterized in that a plug is selected and installed, the plug having a small hole passage serving as an orifice.